EP1771653B1 - Valve for use in a fuel line of a motor vehicle - Google Patents

Valve for use in a fuel line of a motor vehicle Download PDF

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Publication number
EP1771653B1
EP1771653B1 EP20050769882 EP05769882A EP1771653B1 EP 1771653 B1 EP1771653 B1 EP 1771653B1 EP 20050769882 EP20050769882 EP 20050769882 EP 05769882 A EP05769882 A EP 05769882A EP 1771653 B1 EP1771653 B1 EP 1771653B1
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EP
European Patent Office
Prior art keywords
valve
valve body
sealing seat
valve according
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20050769882
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German (de)
French (fr)
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EP1771653A1 (en
Inventor
Lothar Dickenscheid
Dirk MÖHRING
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Continental Automotive GmbH
Original Assignee
Siemens VDO Automotive AG
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Publication date
Application filed by Siemens VDO Automotive AG filed Critical Siemens VDO Automotive AG
Publication of EP1771653A1 publication Critical patent/EP1771653A1/en
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Publication of EP1771653B1 publication Critical patent/EP1771653B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0054—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased

Definitions

  • the invention relates to a valve for use in a fuel-carrying line of a motor vehicle with a sealing seat, a valve seat closing the valve body and a spring device which biases the valve body against the sealing seat, wherein the valve body on its side facing the sealing seat a contour for deflecting the Volume flow over an angle greater than 90 ° and that the outer diameter of the contour is greater than the diameter of the sealing seat.
  • Such valves are in use in fuel lines as a check valve or pressure relief valve.
  • valves have long been known in the art ( DE 197 52 963 A1 ).
  • the valve is often located in a housing having an inlet and an outlet.
  • the inlet has a sealing seat on which the valve body prestressed by the spring device rests and thereby closes the inlet.
  • the fuel flowing through the inlet is thus prevented from continuing to flow. Only when the pressure in the inlet exceeds the force generated by the spring means, the valve body is moved away from the sealing seat. The fuel can now flow around the valve body to the outlet via the now open inlet.
  • valve body disk-shaped components are often used.
  • balls or hemispherical components as a valve body.
  • spherical valve body require a deflection of the fuel flow by an angle of less than 90 °.
  • throttling losses cause these valves have an increasing characteristic.
  • the pressure increases with increasing volume flow.
  • a valve used as a pressure limiter in a feed line leading to an internal combustion engine of a motor vehicle this is a considerable disadvantage, since the pressure in the feed line should be constant independently of the volume flow.
  • the known valves can therefore be used as a function of the increase in the characteristic only for a limited volume flow range.
  • the invention is therefore an object of the invention to provide a valve which ensures a nearly constant pressure in the flow line at different flow rates.
  • the valve should also be simple and easy to install.
  • the object is achieved in that the valve body has on its side facing the sealing seat radially outward a circumferential elevation for deflecting the flow, and that a centrally arranged elevation is arranged in the enclosed by the circumferential elevation surface.
  • valve body directs the volume flow opposite to the pressure forces acting on the valve body.
  • This flow deflection causes additional momentum forces to act on the valve body.
  • this flow deflection can be valves with particularly flat Realizing characteristic curves. This means that the pressure remains constant almost independent of the volume flow.
  • Another key benefit of the valve is that the valve is simple and does not require more parts than conventional valves.
  • the contour of the valve body is advantageously designed such that the deflection of the volume flow in an angular range of 100 ° to 170 °, wherein the angle is related to the axis of the valve body in the flow direction.
  • a simple construction of the valve is also achieved in that the radially inner edge of the radially encircling elevation is designed as a sealing surface, and cooperates with the sealing seat. Additional sealants are therefore not necessary.
  • the deflection of the volume flow is facilitated if the enclosed by the circumferential collection surface of the valve body is concave.
  • the contour of the valve body between the centrally arranged elevation and the circumferential elevation has a continuous course, whereby a particularly low-turbulence and thus loss-free deflection of the volume flow is achieved.
  • valve Due to its simple construction, the valve can be easily integrated into pipes.
  • the design of the valve with a housing also allows the arrangement of the valve anywhere.
  • the spring device is a helical spring. Due to the relatively small diameter of coil springs, the valve can also be designed with a small diameter.
  • the coil spring can be arranged in the flow direction both before and after the valve body.
  • the arrangement of the coil spring relative to the flow direction in front of the valve body has the advantage that this arrangement has a lower vibration behavior of the valve body.
  • the spring device is designed as a plate spring. Lateral recesses in the diaphragm spring thereby ensure the passage of the medium. Such a valve designed in the axial extension requires little space.
  • a valve with a small axial extent is achieved in another embodiment in that the spring device is a leaf spring.
  • the attachment of the leaf spring is advantageously carried on the housing.
  • the valve shown in Fig. 1 is used as a check valve in a fuel line.
  • the valve 1 has a housing 2 which has an inlet 3 and an outlet 4 at its two end faces, wherein the inlet 3 projects into the housing 2.
  • the inlet 3 and the inlet 4 are connectable to not shown line ends of the fuel line.
  • the inlet 3 is closed by a valve body 5, which is pressed by a coil spring 6 against a sealing seat 7 at the inlet 3.
  • the valve body 5 has for this purpose on the side facing away from the sealing seat a receptacle 10 for the coil spring 6.
  • the coil spring 6 is supported on a web 8, which is provided with openings 9 for the passage of the fuel.
  • the valve body 5 On the side facing the sealing seat 7, the valve body 5 has a contour 11, which is formed by a centrally located central elevation 12 and a radially outer circumferential elevation 13. Both elevations 12, 13 are connected to each other by means of a concave surface 14 such that the contour 11 has no paragraphs.
  • the outer diameter of the valve body 5 is greater than the outer diameter of the inlet 3, so that the circumferential elevation 13 in the closed state of the valve 1 surrounds the inlet 3.
  • the inner edge 15 of the peripheral elevation 13 is designed as a sealing surface which rests on the sealing seat 7 of the inlet 3.
  • the valve body 5 If at the inlet 3, the fuel is applied with a greater pressure than the force generated by the coil spring 6, the valve body 5 is moved in the flow direction. The incoming fuel impinges on the central elevation 12, through which it is directed radially outward. The concave surface 14 then directs the flow of fuel in the direction of the circumferential elevation 13, whereby the fuel is deflected relative to the flow direction at an angle of greater than 90 °. In the illustration shown, the fuel flow is deflected at an angle of about 150 °. As a result After the return principle, impulse forces act on the valve body 5. The fuel then flows through the housing 2. The fuel flows via the openings 9 in the web 8 to the outlet 4. The course of the flow is shown by means of arrows.
  • This valve has a nearly constant pressure up to a volume flow of 300 l / h. From a volume flow of 300 l / h up to 500 l / h, the pressure increases approximately linearly by approx. 0.06 bar. Thus, the valve 1 has a horizontal characteristic up to a volume flow of 300 l / h. Only at higher flow rates is an increase in the characteristic curve to be recorded, whereby the increase is still very flat.
  • the valve 1 shown in Fig. 2 substantially corresponds to the structure of the valve 1 in Fig. 1. Only the contour 11 of the valve body 5 differs in that instead of the central elevation, the concave surface 14 is arranged.
  • the valve 1 according to Fig. 3 has a housing 2 with a radial outlet 4.
  • the valve body 5 is mounted in a wall of the housing 2, on which also the spring 16 is supported, which is designed as a plate spring.
  • the spring 16 is designed as a plate spring.
  • no bridge with openings for the fuel flowing through is necessary. Due to the radial outlet 4 and the use of the plate spring 16, the valve 1 in the axial extension requires very little space. In addition, assembly and production are particularly easy.
  • the valve 1 according to FIG. 4 differs from the valve according to FIG. 1 only in that the helical spring 6 is arranged in front of the valve body 5 as seen in the flow direction.
  • the valve 1 shown in Fig. 5 has a leaf spring 17 formed as a spring device, wherein the leaf spring 17 and the valve body 5 are integrally formed.
  • the mounting of the leaf spring 17 is particularly simple by the attachment to the housing 2.
  • valve body 5 in Fig. 6 seals in the region of the inner edge 15 of the circumferential elevation 13 against the sealing seat 7 at the inlet 3 from.
  • the inner edge of an adapted to the sealing seat 7 area in the form of a paragraph which ensures a reliable seal due to its shape design.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Check Valves (AREA)
  • Lift Valve (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention concerns a valve (1) for use in a fuel line of a motor vehicle, comprising a sealing seat (7), a valve body (5) which closes the sealing seat (7) and a spring device (6, 16, 17), which pre-tensions the valve body (5) against the sealing seat (7). The side of the valve body (5) facing the sealing seat (7) has a contour (11) for deflecting the volume flow over an angle of greater than 90° and the outer diameter of the contour (11) is greater than the diameter of the sealing seat (7).

Description

Gegenstand der Erfindung ist ein Ventil für den Einsatz in einer kraftstoffführenden Leitung eines Kraftfahrzeugs mit einem Dichtsitz, einem den Dichtsitz verschließenden Ventilkörper und einer Federvorrichtung, welche den Ventilkörper gegen den Dichtsitz vorspannt, wobei der Ventilkörper auf seiner dem Dichtsitz zugewandten Seite eine Kontur zur Umlenkung des Volumenstroms über einen Winkel von größer 90° besitzt und dass der Außendurchmesser der Kontur größer als der Durchmesser des Dichtsitzes ist. Solche Ventile sind im Einsatz in Kraftstoffleitungen als Rückschlagventil oder Druckbegrenzungsventil.The invention relates to a valve for use in a fuel-carrying line of a motor vehicle with a sealing seat, a valve seat closing the valve body and a spring device which biases the valve body against the sealing seat, wherein the valve body on its side facing the sealing seat a contour for deflecting the Volume flow over an angle greater than 90 ° and that the outer diameter of the contour is greater than the diameter of the sealing seat. Such valves are in use in fuel lines as a check valve or pressure relief valve.

Derartige Ventile sind seit langem bekannter Stand der Technik ( DE 197 52 963 A1 ). Das Ventil ist oftmals in einem Gehäuse angeordnet, welches einen Einlass und einen Auslass besitzt. Der Einlass weist einen Dichtsitz auf, auf dem der von der Federvorrichtung vorgespannte Ventilköper aufsitzt und den Einlass dadurch verschließt. Der durch den Einlass strömende Kraftstoff wird somit am Weiterströmen gehindert. Erst wenn der Druck im Einlass die von der Federeinrichtung erzeugte Kraft übersteigt, wird der Ventilkörper vom Dichtsitz wegbewegt. Über den nunmehr geöffneten Einlass kann der Kraftstoff um den Ventilkörper herum zum Auslass strömen.Such valves have long been known in the art ( DE 197 52 963 A1 ). The valve is often located in a housing having an inlet and an outlet. The inlet has a sealing seat on which the valve body prestressed by the spring device rests and thereby closes the inlet. The fuel flowing through the inlet is thus prevented from continuing to flow. Only when the pressure in the inlet exceeds the force generated by the spring means, the valve body is moved away from the sealing seat. The fuel can now flow around the valve body to the outlet via the now open inlet.

Als Ventilkörper werden vielfach scheibenförmige Bauteile verwendet. Zur Verbesserung der Umströmung des Ventilkörpers ist es weiterhin bekannt, Kugeln oder halbkugelförmige Bauteile als Ventilkörper zu verwenden. Während bei scheibenförmigen Ventilkörpern zur Umströmung des Ventilkörpers der Kraftstoffstrom um 90° umgelenkt wird, erfordern kugelförmige Ventilkörper eine Umlenkung des Kraftstoffstroms um einen Winkel von kleiner 90°. Infolge der Umlenkung auftretende Drosselverluste bewirken, dass diese Ventile eine steigende Kennlinie aufweisen. Das bedeutet, dass mit steigendem Volumenstrom der Druck ansteigt. Insbesondere bei einem als Druckbegrenzer eingesetztem Ventil in einer zu einer Brennkraftmaschine eines Kraftfahrzeugs führenden Vorlaufleitung ist dies ein erheblicher Nachteil, da der Druck in der Vorlaufleitung unabhängig vom Volumenstrom konstant sein soll. Die bekannten Ventile sind daher in Abhängigkeit von dem Anstieg der Kennlinie nur für einen begrenzten Volumenstrombereich einsetzbar.As a valve body disk-shaped components are often used. To improve the flow around the valve body, it is also known to use balls or hemispherical components as a valve body. While with disc-shaped Valve bodies to the flow around the valve body, the fuel flow is deflected by 90 °, spherical valve body require a deflection of the fuel flow by an angle of less than 90 °. As a result of the deflection occur throttling losses cause these valves have an increasing characteristic. This means that the pressure increases with increasing volume flow. Particularly in the case of a valve used as a pressure limiter in a feed line leading to an internal combustion engine of a motor vehicle, this is a considerable disadvantage, since the pressure in the feed line should be constant independently of the volume flow. The known valves can therefore be used as a function of the increase in the characteristic only for a limited volume flow range.

Der Erfindung liegt daher die Aufgabe zugrunde, ein Ventil zu schaffen, welches bei verschiedenen Volumenströmen einen nahezu konstanten Druck in der Vorlaufleitung gewährleistet. Das Ventil soll darüber hinaus einfach aufgebaut und leicht zu montieren sein.The invention is therefore an object of the invention to provide a valve which ensures a nearly constant pressure in the flow line at different flow rates. The valve should also be simple and easy to install.

Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass der Ventilkörper auf seiner dem Dichtsitz zugewandten Seite radial außen eine umlaufende Erhebung zum Umlenken der Strömung besitzt, und dass eine zentral angeordnete Erhebung in der von der umlaufenden Erhebung eingeschlossenen Fläche angeordnet ist.According to the invention the object is achieved in that the valve body has on its side facing the sealing seat radially outward a circumferential elevation for deflecting the flow, and that a centrally arranged elevation is arranged in the enclosed by the circumferential elevation surface.

Mit dieser Kontur leitet der Ventilkörper den Volumenstrom entgegengesetzt zu den Druckkräften, die auf den Ventilkörper wirken. Diese Strömungsumlenkung bewirkt, dass zusätzliche Impulskräfte auf den Ventilkörper einwirken. Als Folge dieser Strömungsumlenkung lassen sich Ventile mit besonders flachen Kennlinien realisieren. Das bedeutet, dass der Druck nahezu unabhängig vom Volumenstrom konstant bleibt. Ein weiterer wesentlicher Vorteil des Ventils besteht darin, dass das Ventil einfach aufgebaut ist und nicht mehr Teile als herkömmliche Ventile benötigt.With this contour, the valve body directs the volume flow opposite to the pressure forces acting on the valve body. This flow deflection causes additional momentum forces to act on the valve body. As a result of this flow deflection can be valves with particularly flat Realizing characteristic curves. This means that the pressure remains constant almost independent of the volume flow. Another key benefit of the valve is that the valve is simple and does not require more parts than conventional valves.

Die Kontur des Ventilkörpers ist vorteilhafterweise derart ausgebildet, dass die Umlenkung des Volumenstroms in einem Winkelbereich von 100° bis 170° erfolgt, wobei der Winkel auf die Achse des Ventilkörpers in Strömungsrichtung bezogen ist.The contour of the valve body is advantageously designed such that the deflection of the volume flow in an angular range of 100 ° to 170 °, wherein the angle is related to the axis of the valve body in the flow direction.

Für die Ausbildung einer besonders flachen Kennlinie des Ventils hat sich eine Kontur des Ventilkörpers erwiesen, welche den Volumenstrom in einem Winkelbereich von 120° bis 150° umlenkt.For the formation of a particularly flat characteristic of the valve, a contour of the valve body has been found, which deflects the flow in an angular range of 120 ° to 150 °.

Ein einfacher Aufbau des Ventils wird auch dadurch erreicht, dass die radial innen liegende Flanke der radial umlaufenden Erhebung als Dichtfläche ausgebildet ist, und mit dem Dichtsitz zusammenwirkt. Zusätzliche Dichtmittel sind somit nicht notwendig.A simple construction of the valve is also achieved in that the radially inner edge of the radially encircling elevation is designed as a sealing surface, and cooperates with the sealing seat. Additional sealants are therefore not necessary.

Es ist aber auch denkbar, zur besseren Abdichtung an der radial innen liegenden Flanke einen Bereich vorzusehen, der durch spezielle Formelemente dem am Einlass befindlichen Dichtsitz angepasst ist. Solche Formelemente können beispielsweise ein Absatz oder eine Dichtlippe sein. Aufgrund ihrer relativ geringen Abmessungen haben derartige Formelemente nahezu keinen störenden Einfluss auf den umgelenkten Volumenstrom.However, it is also conceivable to provide a region for better sealing on the radially inner flank, which is adapted to the inlet seat located at the inlet by means of special shaped elements. Such form elements may be, for example, a shoulder or a sealing lip. Due to their relatively small dimensions, such shaped elements have virtually no disturbing influence on the diverted volume flow.

Das Umlenken des Volumenstroms wird erleichtert, wenn die von der umlaufenden Erhebung eingeschlossene Fläche des Ventilkörpers konkav ausgebildet ist.The deflection of the volume flow is facilitated if the enclosed by the circumferential collection surface of the valve body is concave.

In einer weiteren vorteilhaften Ausbildung besitzt die Kontur des Ventilkörpers zwischen der zentral angeordneten Erhebung und der umlaufenden Erhebung einen kontinuierlichen Verlauf, wodurch eine besonders verwirbelungsarme und damit verlustfreie Umlenkung des Volumenstroms erreicht wird.In a further advantageous embodiment, the contour of the valve body between the centrally arranged elevation and the circumferential elevation has a continuous course, whereby a particularly low-turbulence and thus loss-free deflection of the volume flow is achieved.

Aufgrund des einfachen Aufbaus lässt sich das Ventil problemlos in Leitungen integrieren. Die Ausbildung des Ventils mit einem Gehäuse ermöglicht darüber hinaus die Anordnung des Ventils an beliebigen Stellen.Due to its simple construction, the valve can be easily integrated into pipes. The design of the valve with a housing also allows the arrangement of the valve anywhere.

In einer besonders einfachen Ausführung ist die Federvorrichtung eine Schraubenfeder. Aufgrund des relativ geringen Durchmessers von Schraubenfedern kann das Ventil ebenfalls mit einem geringen Durchmesser gestaltet werden.In a particularly simple embodiment, the spring device is a helical spring. Due to the relatively small diameter of coil springs, the valve can also be designed with a small diameter.

Ein weiterer Vorteil besteht darin, dass die Schraubenfeder in Strömungsrichtung sowohl vor als auch nach dem Ventilkörper angeordnet werden kann. Die Anordnung der Schraubenfeder bezogen auf die Strömungsrichtung vor dem Ventilkörper hat dabei den Vorteil, dass diese Anordnung ein geringeres Schwingungsverhalten des Ventilkörpers aufweist.Another advantage is that the coil spring can be arranged in the flow direction both before and after the valve body. The arrangement of the coil spring relative to the flow direction in front of the valve body has the advantage that this arrangement has a lower vibration behavior of the valve body.

In einer weiteren Ausgestaltung ist die Federvorrichtung als Tellerfeder ausgebildet. Seitliche Ausnehmungen in der Tellerfeder gewährleisten dabei den Durchtritt des Mediums. Ein derart gestaltetes Ventil benötigt in axialer Erstreckung besonders wenig Bauraum.In a further embodiment, the spring device is designed as a plate spring. Lateral recesses in the diaphragm spring thereby ensure the passage of the medium. Such a valve designed in the axial extension requires little space.

Ein Ventil mit einer geringen axialen Erstreckung wird in einer anderen Ausgestaltung dadurch erreicht, dass die Federvorrichtung eine Blattfeder ist. Die Befestigung der Blattfeder erfolgt vorteilhafterweise am Gehäuse.A valve with a small axial extent is achieved in another embodiment in that the spring device is a leaf spring. The attachment of the leaf spring is advantageously carried on the housing.

Die Erfindung wird an mehreren Ausführungsbeispielen erläutert. Dabei zeigen

Fig. 1
eine schematische Darstellung des erfindungsgemäßen Ventils im Schnitt,
Fig. 2
ein Beispiel eines nicht erfindungsgemäßen Ventils,
Fig. 3, 4
weitere Ausgestaltungen des Ventils mit verschiedenen Federvorrichtungen und Gehäuseausbildungen,
Fig. 5
eine Ausgestaltung eines nicht erfindundsgemäßen Ventils mit einer Blattfeder und
Fig. 6
eine vergrößerte Darstellung des Ventilkörpers und des Dichtsitzes.
The invention will be explained with reference to several embodiments. Show
Fig. 1
a schematic representation of the valve according to the invention in section,
Fig. 2
an example of a valve not according to the invention,
Fig. 3, 4
further embodiments of the valve with various spring devices and housing designs,
Fig. 5
An embodiment of a non-inventively valve with a leaf spring and
Fig. 6
an enlarged view of the valve body and the sealing seat.

Das in Fig. 1 dargestellte Ventil wird als Rückschlagventil in einer Kraftstoffleitung eingesetzt. Das Ventil 1 besitzt ein Gehäuse 2, welches an seinen beiden Stirnseiten einen Einlass 3 und einen Auslass 4 aufweist, wobei der Einlass 3 in das Gehäuse 2 hineinragt. Der Einlass 3 und der Einlass 4 sind mit nicht dargestellten Leitungsenden der Kraftstoffleitung verbindbar. Der Einlass 3 wird von einem Ventilkörper 5 verschlossen, der von einer Schraubenfeder 6 gegen einen Dichtsitz 7 am Einlass 3 gepresst wird. Der Ventilkörper 5 besitzt hierzu auf der dem Dichtsitz abgewandten Seite eine Aufnahme 10 für die Schraubenfeder 6. An ihrem dem Ventilkörper 5 abgewandten Ende stützt sich die Schraubenfeder 6 an einem Steg 8 ab, der mit Durchbrüchen 9 zum Durchlass des Kraftstoffs versehen ist.The valve shown in Fig. 1 is used as a check valve in a fuel line. The valve 1 has a housing 2 which has an inlet 3 and an outlet 4 at its two end faces, wherein the inlet 3 projects into the housing 2. The inlet 3 and the inlet 4 are connectable to not shown line ends of the fuel line. The inlet 3 is closed by a valve body 5, which is pressed by a coil spring 6 against a sealing seat 7 at the inlet 3. The valve body 5 has for this purpose on the side facing away from the sealing seat a receptacle 10 for the coil spring 6. At its end remote from the valve body 5, the coil spring 6 is supported on a web 8, which is provided with openings 9 for the passage of the fuel.

Auf der dem Dichtsitz 7 zugewandten Seite weist der Ventilkörper 5 eine Kontur 11 auf, die von einer mittig angeordneten zentralen Erhebung 12 und einer radial außen angeordneten umlaufenden Erhebung 13 gebildet wird. Beide Erhebungen 12, 13 sind mittels einer konkav ausgebildeten Fläche 14 derart miteinander verbunden, dass die Kontur 11 keinerlei Absätze aufweist. Der Außendurchmesser des Ventilkörpers 5 ist dabei größer als der Außendurchmesser des Einlasses 3, so dass die umlaufende Erhebung 13 im geschlossenen Zustand des Ventils 1 den Einlass 3 umgreift. Die innere Flanke 15 der umlaufenden Erhebung 13 ist dabei als Dichtfläche ausgebildet, die am Dichtsitz 7 des Einlasses 3 anliegt.On the side facing the sealing seat 7, the valve body 5 has a contour 11, which is formed by a centrally located central elevation 12 and a radially outer circumferential elevation 13. Both elevations 12, 13 are connected to each other by means of a concave surface 14 such that the contour 11 has no paragraphs. The outer diameter of the valve body 5 is greater than the outer diameter of the inlet 3, so that the circumferential elevation 13 in the closed state of the valve 1 surrounds the inlet 3. The inner edge 15 of the peripheral elevation 13 is designed as a sealing surface which rests on the sealing seat 7 of the inlet 3.

Sofern am Einlass 3 der Kraftstoff mit einem größeren Druck als die von der Schraubenfeder 6 erzeugte Kraft anliegt, wird der Ventilkörper 5 in Strömungsrichtung bewegt. Der einströmende Kraftstoff trifft auf die zentrale Erhebung 12, durch die er radial nach außen geleitet wird. Die konkav ausgebildete Fläche 14 leitet anschließend den Kraftstoffstrom in Richtung der umlaufenden Erhebung 13, wodurch der Kraftstoff bezogen auf die Strömungsrichtung in einem Winkel von größer 90° umgelenkt wird. In der gezeigten Darstellung wird der Kraftstoffstrom in einem Winkel von ca. 150° umgelenkt. Infolge der Umlenkung wirken nach dem Rückstossprinzip Impulskräfte auf den Ventilkörper 5. Anschließend durchströmt der Kraftstoff das Gehäuse 2. Über die Durchbrüche 9 im Steg 8 strömt der Kraftstoff weiter zum Auslass 4. Der Verlauf der Strömung ist mittels Pfeilen dargestellt. Dieses Ventil besitzt bis zu einem Volumenstrom von 300 l/h einen nahezu konstanten Druck. Ab einem Volumenstroms von 300 l/h bis zu 500 l/h steigt der Druck annähernd linear um ca. 0,06 bar. Damit weist das Ventil 1 bis zu einem Volumenstrom von 300 l/h eine waagerechte Kennlinie auf. Erst bei größeren Durchflüssen ist ein Anstieg der Kennlinie zu verzeichnen, wobei der Anstieg immer noch sehr flach ist.If at the inlet 3, the fuel is applied with a greater pressure than the force generated by the coil spring 6, the valve body 5 is moved in the flow direction. The incoming fuel impinges on the central elevation 12, through which it is directed radially outward. The concave surface 14 then directs the flow of fuel in the direction of the circumferential elevation 13, whereby the fuel is deflected relative to the flow direction at an angle of greater than 90 °. In the illustration shown, the fuel flow is deflected at an angle of about 150 °. As a result After the return principle, impulse forces act on the valve body 5. The fuel then flows through the housing 2. The fuel flows via the openings 9 in the web 8 to the outlet 4. The course of the flow is shown by means of arrows. This valve has a nearly constant pressure up to a volume flow of 300 l / h. From a volume flow of 300 l / h up to 500 l / h, the pressure increases approximately linearly by approx. 0.06 bar. Thus, the valve 1 has a horizontal characteristic up to a volume flow of 300 l / h. Only at higher flow rates is an increase in the characteristic curve to be recorded, whereby the increase is still very flat.

Das in Fig. 2 gezeigt Ventil 1 entspricht im Wesentlichen dem Aufbau des Ventils 1 in Fig. 1. Lediglich die Kontur 11 des Ventilkörpers 5 unterscheidet sich dahingehend, dass anstelle der zentralen Erhebung die konkav ausgebildete Fläche 14 angeordnet ist.The valve 1 shown in Fig. 2 substantially corresponds to the structure of the valve 1 in Fig. 1. Only the contour 11 of the valve body 5 differs in that instead of the central elevation, the concave surface 14 is arranged.

Das Ventil 1 nach Fig. 3 besitzt ein Gehäuse 2 mit einem radialen Auslass 4. der Ventilkörper 5 ist in einer Wand des Gehäuses 2 gelagert, an der sich auch die Feder 16 abstützt, die als Tellerfeder ausgebildet ist. Bei dieser Ausgestaltung ist kein Steg mit Durchbrüchen für den durchströmenden Kraftstoff notwendig. Bedingt durch den radialen Auslass 4 und der Verwendung der Tellerfeder 16 benötigt das Ventil 1 in axialer Erstreckung besonders wenig Bauraum. Darüber hinaus gestalten sich Montage und Herstellung besonders einfach.The valve 1 according to Fig. 3 has a housing 2 with a radial outlet 4. The valve body 5 is mounted in a wall of the housing 2, on which also the spring 16 is supported, which is designed as a plate spring. In this embodiment, no bridge with openings for the fuel flowing through is necessary. Due to the radial outlet 4 and the use of the plate spring 16, the valve 1 in the axial extension requires very little space. In addition, assembly and production are particularly easy.

Das Ventil 1 nach Fig. 4 unterscheidet sich von dem Ventil gemäß Fig. 1 lediglich dadurch, dass die Schraubenfeder 6 in Strömungsrichtung gesehen vor dem Ventilkörper 5 angeordnet ist.The valve 1 according to FIG. 4 differs from the valve according to FIG. 1 only in that the helical spring 6 is arranged in front of the valve body 5 as seen in the flow direction.

Das in Fig. 5 gezeigte Ventil 1 besitzt eine als Blattfeder 17 ausgebildete Federvorrichtung, wobei die Blattfeder 17 und der Ventilkörper 5 einteilig ausgebildet sind. Die Montage der Blattfeder 17 gestaltet sich durch die Befestigung am Gehäuse 2 besonders einfach.The valve 1 shown in Fig. 5 has a leaf spring 17 formed as a spring device, wherein the leaf spring 17 and the valve body 5 are integrally formed. The mounting of the leaf spring 17 is particularly simple by the attachment to the housing 2.

Der Ventilkörper 5 in Fig. 6 dichtet im Bereich der inneren Flanke 15 der umlaufenden Erhebung 13 gegen den Dichtsitz 7 am Einlass 3 ab. Dazu weist die innere Flanke einen an den Dichtsitz 7 angepassten Bereich in Form eines Absatzes auf, der aufgrund seiner Formgestaltung eine zuverlässige Abdichtung gewährleistet.The valve body 5 in Fig. 6 seals in the region of the inner edge 15 of the circumferential elevation 13 against the sealing seat 7 at the inlet 3 from. For this purpose, the inner edge of an adapted to the sealing seat 7 area in the form of a paragraph, which ensures a reliable seal due to its shape design.

Claims (14)

  1. Valve (1) for use in a fuel line of a motor vehicle, comprising a sealing seat (7), a valve body (5) which closes the sealing seat (7), and a spring device (16, 17), which pretensions the valve body (5) against the sealing seat, the valve body (5), on its side facing the sealing seat (7), having a contour (11) for deflecting the volume flow by an angle of more than 90°, and the outside diameter of the contour (11) being greater than the diameter of the sealing seat (7), characterized in that on its side facing the sealing seat (7) the valve body (5) has a radially outer peripheral elevation (13) for deflecting the flow, and in that the face (14) enclosed by the peripheral elevation (13) has a centrally arranged elevation (12).
  2. Valve according to Claim 1, characterized in that the contour (11) of the valve body (5) is designed to deflect the flow within an angular range of 100° to 170°, in particular between 120° and 150°.
  3. Valve according to Claim 1 or 2, characterized in that the radially inner flank (15) of the radially peripheral elevation (13) takes the form of a sealing face for interaction with the sealing seat (7).
  4. Valve according to Claim 3, characterized in that the radially inner flank (15) of the radially peripheral elevation (13) has an area (18) which conforms to the shape of the sealing seat (7).
  5. Valve according to at least one of the preceding claims, characterized in that the face (14) of the valve body (5) enclosed by the peripheral elevation (13) is of concave design.
  6. Valve according to at least one of the preceding claims, characterized in that the contour (11) between the peripheral elevation (13) and the centrally arranged elevation (12) has a continuous profile.
  7. Valve according to at least one of the preceding claims, characterized in that the valve (1) is arranged in a housing (2).
  8. Valve according to at least one of the preceding claims, characterized in that the spring device is a helical coil spring (6).
  9. Valve according to at least one of the preceding claims, characterized in that the helical coil spring (6) is arranged downstream of the valve body (5) in the direction of flow.
  10. Valve according to at least one of the preceding Claims 1 to 10, characterized in that the helical coil spring (6) is arranged upstream of the valve body (5) in the direction of flow.
  11. Valve according to at least one of the preceding Claims 1 to 9, characterized in that the spring device is a disk spring (16).
  12. Valve according to at least one of the preceding Claims 1 to 9, characterized in that the spring device is a leaf spring (17).
  13. Valve according to Claim 12, characterized in that the leaf spring (17) is fixed to the housing (2).
  14. Valve according to Claim 12, characterized in that the leaf spring (17) and the valve body (5) are integrally formed.
EP20050769882 2004-07-30 2005-07-26 Valve for use in a fuel line of a motor vehicle Not-in-force EP1771653B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410037419 DE102004037419B3 (en) 2004-07-30 2004-07-30 Valve for use in a fuel-carrying line of a motor vehicle
PCT/EP2005/053640 WO2006013176A1 (en) 2004-07-30 2005-07-26 Valve for use in a fuel line of a motor vehicle

Publications (2)

Publication Number Publication Date
EP1771653A1 EP1771653A1 (en) 2007-04-11
EP1771653B1 true EP1771653B1 (en) 2007-12-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050769882 Not-in-force EP1771653B1 (en) 2004-07-30 2005-07-26 Valve for use in a fuel line of a motor vehicle

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US (2) US20080023079A1 (en)
EP (1) EP1771653B1 (en)
JP (1) JP4763694B2 (en)
KR (1) KR101214703B1 (en)
CN (1) CN100591911C (en)
DE (2) DE102004037419B3 (en)
ES (1) ES2296214T3 (en)
WO (1) WO2006013176A1 (en)

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US20130312852A1 (en) 2013-11-28
ES2296214T3 (en) 2008-04-16
CN100591911C (en) 2010-02-24
CN1985088A (en) 2007-06-20
US20080023079A1 (en) 2008-01-31
JP4763694B2 (en) 2011-08-31
EP1771653A1 (en) 2007-04-11
DE102004037419B3 (en) 2006-02-16
WO2006013176A1 (en) 2006-02-09
KR20070042978A (en) 2007-04-24
JP2008508481A (en) 2008-03-21
KR101214703B1 (en) 2012-12-21
DE502005002311D1 (en) 2008-01-31

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